Stacking machine



May 6, 1952 w. J. HORN STACKING MACHINE 3 Sheets-Sheet l Filed July 25, 1949 May 6, 1952 w. J. HORN STACKING MACHINE Filed July 25, 1949 3 Sheets-Sheet 2 49 3 Tlfl ./N VEN T012 l2 Walter J Horn @W ffii? W. J. HORN STACKING MACHINE May 6, 1952 I5 Sheets-Sheet 5 Filed July 25, 1949 Patented May 6, 1952 STACKING MACHINE Walter J. Horn, Fort Dodge, Iowa, assignor to Horn Manufacturing Company, Fort Dodge, Iowa, a corporation of Iowa Application July 25, 1949, Serial No. 106,694

(Cl. .2M- 82) 3 Claims.

This invention relates generally to loading machines and in particular to a push-olf rake for a stacking machine.

An object of this invention is to provide an improved stacking machine.

A further object of this invention is to provide a stacking machine having a push-olf rake in which a rear gate is hydraulically operated and adapted to be moved at a relatively fast rate of speed during a push-olf operation.

Yet another object of4 this invention is to provide a push-ofi rake having a rear gate hydraulically operated through a leverage system such that the actuating force applied on the gate is a maximum at the initiation of movement of the gate for a pushing operation.

A still further object of this invention is to provide a push-off rake of a simple and compact construction and having a rear movable gate which is positive and eicient in operation, and readily and easily controlled.

A feature of this invention is found in the provision of a stacking machine having a push-off rake in which a transverse rock shaft is mounted at the rear end of the rake ata position substantially level with the top side of a rear gate supported on the rake for movement longitudinally thereof fA pair of rock arms on the shaft, swingable downwardly between rearwardly inclined and forwardly inclined positions, have their lfree ends pivoted to the rear ends of Y-shape arms extended rearwardly from the gate. A double acting hydraulic cylinder, for rocking the shaft, is connected to the shaft through a double leverage system which provides for a maximum leverage action on the gate to initiate its push-off movement, a rapid movement of the gate to its push-off position, and a positive leverage action tofinitiate the return movement of the gate.

vFurther objects, features, and advantages of this invention will become apparent from the following description when taken in connection with the accompanying drawings, 1n which:

Fig. 1 is a rear perspective view of the pushoff rake of this invention shown in assembly relation with the lift arms of a tractor-loader attachment;

Fig. 2 is a plan View of the assembly shown in Fig. 1;

Fig. 3 is a transverse sectional view as seen on the line 3-3 in Fig. 2;

Fig. 4 is a longitudinal sectional view taken on the line 4-4 in Fig. 2;

Fig. 5 is an enlarged sectional VeW as seen on vthe line 5 5 1n Fig. 3; and

Fig. 6 is a foreshortened sectional View as taken along the line 6--6 in Fig. 4.

With reference to the drawings the push-01T rake of this invention is illustrated in Figs. 1 and 2 in assembly relation with a pair of booms or lift arms IUI, which are arranged at opposite sides of a tractor I I. The rear ends (not shown) of the arms II) are pivotally supported on the tractor to provide for a pivotal up and down movement of the arms. The lift mechanism for raising'and lowering the arms I0 includes a pair of oppositely arranged hydraulic cylinders I2, corresponding to the arms III, and pivotally mounted at I3 on the tractor II. The cylinder pistons I 4 carry pulleys I6 at their outer or upper ends for movably supporting cables I'I, each of which is attached at one end I8 to a corresponding lift arm IB, and secured at its opposite end (not shown) to the tractor. Fluid under pressure is supplied to the cylinders I2 from a pump unit (not shown) mounted on and operated by the tractor.

The push-off rake of this invention includes a main frame or base of an angle iron construction and indicated generally as I9. The frame I9 is of a substantially rectangular shape and is" provided at its opposite ends with pairs of upright supports 2I spaced transversely of the frame I9 or longitudinally of the rake. suitably secured to the lower side of the frame I9 are a plurality of spaced bottom tines 22 having their of the rear gate 24 (Fig. 6) rests on the top sides front ends projected forwardly from the base I9. Side tines 23 are mounted upon and extended forwardly from the upright supports 2|.

A push-off or rear gate, designated generally z as 24 (Figs. 1 and 4), includes a plurality of vertically spaced flat board members 26 positioned transversely of the rake and mounted on upright' angle members 21, illustrated in Fig.` 2 as being four in number. The lower board member 26a of the bottom tines 22 to slidably support the gate 24 for movement longitudinally of the rake' between positions defined by the front ends of -the tines 22 and the forward side of the main f rights indicated at 21a, with the guides 28 being projected downwardly from the board 26a and of a size to-loosely receive the bottom tines `indicated at 22a.

To move the gate 24 longitudinally of the rake,-

there is provided an upright frame located rearwardly of the gate 24 and comprised of a pair of side members 29 tapered inwardly toward their upper ends and of a generally channel shape in transverse cross section (Figs. 1, 4 and 5). The upright members 29 are located centrally of the main frame I9 in a longitudinally spaced relation and are provided at opposite sides of their lower ends 3| with angle base plates 32. The lower ends 5I of the upright frame members 29 are of a width corresponding substantially to the distance between the side members 33 of the main frame I9 so as to be receivable therebetween, with corresponding vertical legs and on the base plates 32 and side members 33, respectively, in a back to back relation. The horizontal legs 36 of the base plates 32 rest on the top sides of the bottom tine`s, indicated at 221), and the corresponding upright legs 30 and 35 of the base plates 32 and side members 33, are secured together as by bolts 31.

Adjustable brace members 38 (Fig. 1) are connected at 39, adjacent the upper ends of the upright members 29, while their lower ends are connected at 4I to upright projections 42 on a transverse brace 43 connected between the forward ends of the lift arms I9. A transverse tubular frame member 44 (Figs. 4 and 5) is extended through the lower ends 3I of the upright members 29 so that its opposite ends' 46 project laterally outwardly from the members 29.

Each projected end 46 of the tubular frame member 44 carries a pair of rearwardly extended longitudinally spaced lugs 41 adapted to receive therebetween a front end 49 of a lift arm It.'

The lift arms I9 are connected with the lugs 41 by bolts 49 extended therethrough. It is seen, therefore, that the push-off rake is maintained against tipping movement relative to the arms I0 by a three-point supporting action comprising the opposite end connections of the adjustable braces 38 and the lift arm connection 49.

Each upright member 29 (Figs. 1 and 4) has at its upper end a pair of transversely spaced forwardly extended projections 5I for receiving therebetween a corresponding upright projection 52 carried cn a transverse rock shaft 53, the opposite ends 54 of which project laterally outwardly from the upright members 29. The projections 5I and 52 are pivotally connected at 56 so that the shaft 53 on rocking movement in a clockwise direction, as viewed in Fig. 4, is also moved forwardly and upwardly relative to the upright frame members 29.

Each end 54 of the rock shaft 53 (Fig. l) has an upright projection 51 which is pivotally connected at 58 with the upper end of a brace member 59, having its lower end 66 suitably secured to an end frame 2| of the main frame I9. The pivots 58 and 56 are in axial alignment longitudinally of the rock shaft 53 to provide for its free swinging movement relative to the upright frame members 29.

Mounted at opposite ends of the tubular rock shaft 53 (Figs. 1 and 3) are a pair of rock arms 6I of a substantially channel shape in transverse cross section, with the arms being arranged relative to the rock shaft 53 so as to be swingable downwardly from rearwardly inclined positions to forwardly inclined positions as the rock shaft is moved forwardly and upwardly on its pivot supports 56 and 58. The free ends of the rock arms 6I are pivotally connected Vat 62 with the rear ends of Y-shape arm structures 63, the forward ends of which structures are connected at 4 64 at vertically spaced positions on the center upright angles 21a. It is thus seen that the rock arms 6I and Y-arm structures 63 comprise articulated arm systems which are movable to forwardly extended or open positions, and to rearwardly closed or collapsed positions in response to the rocking movement of the shaft 53, as will later appear.

The rock shaft 53 is actuated by means including an upright guide member 66 of a rod construction (Figs. 1, 3 and 4) located intermediate the upright frame members 29 and having its lower end pivoted at 61 between a pair of projections 68 extended forwardly from the tubular frame member 44. Slidably supported on the guide member 66 for up and down movement is a sleeve or slide member 69 of a tubular construction, the upper end of which is pivotally connected at 1I with the free end 12 of a lever 13, the opposite end 14 of which is mounted on the rock shaft 53. A second lever 16, mounted on the rock shaft 53, in a vertical plane common to the lever 13, has its free end pivoted at 11 to the outer or upper end of a double acting piston 18 operatively associated with an upright cylinder 19. The lower end 3| of the cylinder 19 is pivotally supported at 82 on a forward projection 83 carried adjacent the lower end of the slide member 69.

The rock shaft levers 13 and 16 are in a vertical plane extended longitudinally of the rake unit and constitute a bell crank member integrally formed with the rock shaft 13, with the lever 13 being of a longer length than the lever 16. As best appears in Fig. 4, when the rock arms 5I and arm structures 63 are in their rearwardly folded positions, the gate 24 is in its rear-most or normal position adjacent the front side member 33 of the main frame I9. At this position of the gate 24 the piston 18 is retracted within the cylinder 19 and the slide member 69 is in its outermost position extended upwardly relative to the guide rod 56. With the slide member 69 extended. the long lever arm 13 is inclined upwardly and rearwardly from the rock shaft 53, while the shorter lever arm 16 is extended substantially vertically downward from the rock shaft.

In the operation of the push-off rake of this invention, assume the gate 24 to be in its rest or normal position, as shown in full lines in Fig. 4. On the supply of fluid under pressure to the lower end of the cylinder 19 through a fluid conduit 86 which is suitably connected with the oilsupply unit mounted on the tractor I I, the cylinder 19 is initially moved downward relative to the piston 18, as a result of the downward projection of the lever arm 16. In other words. when the lever arm 16 is in its full-line position shown in Fig. 4, the pivots 56 and 11 are in substantially a common vertical plane extended through the longitudinal axis of the rock shaft 53. As a result, the lever 16 is substantially locked against upward movement in response to any pressure applied thereon by the piston 18. The downward movement of the cylinder 19 in turn provides for a downward movement of the slide member 69, whereby the cylinder pressure is applied through the member 69 and long lever 13 on the rock shaft A53 to rock the same about its pivots 56 and 58.

As a result, a maximum leverage action is applied on the shaft 53 to initiate the forward movement of the gate 24 from its full-line rest position in Fig. 4 to its push-off position, shown in dotted lines in the same figure. Further, the

initial rocking movement of the shaft 53, in a clockwise direction as seen in Fig. 4, 'moves the pivot connection 11 of the piston 18 with the lever 16 forwardly out of vertical alignment with the pivots 56 and 58, whereby to release the piston 18 for extension from the cylinder 19. Thus after movement of the gate 24 has been initiated, its continued movement to a push-off position takes place by the leverage action of both of the levers 13 and 16. This push-off position of the gate 24 is defined by a fully extended position of the -pis ton 18 relative to the cylinder 19.

With the piston 18 fully extended, and as illustrated in Fig. 4, the rock arms 6| are inclined forwardly and downwardly from the rock shaft 53 and the arm structures 63 are projected forwardly Ifrom the rock arms 6l. Further, it will be noted that the lever arm 13 is extended substantially vertically downward from the rock shaft 53, while the shorter lever arm 16 is inclined upwardly and forwardly from the rock shaft 53.

To return the gate 24 from its push-off position to its rest position adjacent the main frame I9, fluid under pressure is supplied to the upper end of the cylinder 19 through a fluid conduit 88. Since the lever 13 is in substantial longitudinal alignment with the slide member 69 and guide member 66, this return movement of the gate 24 is initiated primarily by the leverage action of the shorter leverl 16 on the rock shaft 53. It is to be noted that this leverage action of the short lever 16 is complemented by the leverage action of the upright projections 52, through which the shaft 53 is pivoted at 56 on the upright frame members 29.

After the return movement of the gate 24 has been initiated, the levers 13 and 16 act concurrently to rock the shaft 53 in a counter-clockwise direction, as viewed in Fig. 4, with the leverage action of the lever 16 becoming progressively less, and the action of the lever 13 progressively greater, as the gate 24 approaches its rest position.

It is seen, therefore, that the movement of the gate 24 from its rest position to its push-off position is initiated primarily by the action of the lever 13, and with the action of the lever 13 to move the gate 24 being progressively decreased as the gate approaches its push-off position. However, with a decrease in the action of the lever 13 on the shaft 53, there is a corresponding increase in the action of the lever 16 on the rock shaft, so that the gate 24 is positively moved to its push-off position, and with its approach to such position being at a slower rate relative to its previous rate of movement on the tines 22.

Conversely, the rate of return movement of the gate 24, as initiated by the lever 16, is less than its rate of movement as provided by the action of the lever 13, after the lever 13 has been moved rearwardly from its position in substantial alignment with the slide member 69.

Since the supply of fluid under pressure to the conduits 86 and 88 to the double acting cylinder 19 is accomplished through a simple finger actuated valve control (not shown), the movement of the gate 24 longitudinally of the tines 22 is conveniently and simply accomplished, and with this movement being both positive and relatively fast by virtue of the complementary action of the levers 13 and 16. It is further apparent that the assembly'of the rake unit on the lift arms i9 is capable of being easily made by one man and, after'adjustment of the braces 3B hasbeen made, consists only in handling the bolt connections 39 and 4|. Adjustment of the brace members 38 provides for a tipping movement of the front ends of the tines 22 to positions substantially six inches below a level or horizontal position of the tines, to a position about three inches above a horizontalfposition of the tines. The adjustment or tilt of the tines 22 is determined from the kind of material to be handled by the rake unit.

Furthenit is to .be understood that in the loading of the rake unit, the gate 24 is in its rest or normal position shown in full lines in Fig. 4. The

rake is then filled by a usual bucking operation,. after which the loaded rake is elevated to a desired position by the operation of the lift arms I0, and while in such elevated position, the gate 24 is moved to its push-off position to unload the rake.

Although the invention has been described with respect to a preferred embodiment thereof, it is to be understood that it is not to be so limited since changes can be made therein which are within the full intended scope of this invention, as defined by the appended claims.

I claim:

1. In a stacking machine including a push off rake, an upright push gate movably supported for movement longitudinally of said rake, means for moving said push gate including an upright frame on said rake located rearwardly of the push gate, a rock shaft on said upright frame having a pair of rock arms at opposite ends thereof, a pair of rearwardly extended arms on said push gate having their rear ends pivoted to the free ends of said rock arms, an upright guide rod pivoted at its lower end on said rake, a sleeve member movable on said guide rod, a first lever xed at one end on said rock shaft, means pivotally connecting the other end of said first lever with said sleeve, an upright hydraulic cylinder pivotally supported at its lower end on said sleeve, a piston for said cylinder, and a second lever on said rock shaft pivotally connected at its free end to the outer end of said piston.

2. In a stacking machine, a push-off rake including a rear gatemovable longitudinally of said rake, a transverse rock shaft supported on said rake rearwardly of said gate at a position adjacent the upper end thereof, a pair of downwardly extended rock arms on said rock shaft movable to opposite sides of a vertical plane through the axis of said rock shaft, a pair of rearwardly extended arms on said gate having their rear ends pivoted to the free ends of said rock arms, means for rocking said shaft to move said gate including an upright slide member, means supporting said slide member for up and down movement, an upright cylinder pivotally supported at its lower end on said slide member,

a piston for said cylinder, a pair of levers mounted' on said rock shaft in a substantially common vertical plane, with one of said levers being longer than the other lever, said levers being relatively arranged such that when said rock arms are extended downwardly and rearwardly the longer lever is inclined upwardly and rearwardly and the shorter lever is `extended downwardly, means pivotally connecting the free end of said shorter lever with said piston, and other means pivotally connecting the free end Y of said longer lever with said slide member.

3. In a stacking machine, a push off rake including a rear gate movable longitudinally of `said rake, a transverse Yrock shaft supported on said rake rearwardly of said gate, a rearwardly extended rock arm `on said shaft, means movably connecting the free end of said rock arm with said gate, means for rocking said shaft to move said gate including a slide member, means guiding said slide member for up and down movement, an upright cylinder pivotally supported at its lower end on said slide member, a piston for said cylinder, a pair of levers mounted on said rock shaft in a substantially common vertical plane, means pivotally connecting one of said levers with said piston, and other means pivotally connecting the other of said levers with said slide member.

WALTER J. HORN.

8 REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,397,045 Richey Mar. 19, 1946 2,397,046 Richey Mar. 19. ,1946 2,418,661 Palm Apr. 8, 1947 2,496,039 Crawford Jan. 31, 1950 2,497,385 Young et al Feb. 14, 1950 

